Roller bearing



Nov. 10, 1942. L. R. HElM ROLLER BEARING Original Filed July 18} 1934INVENTOR Lewis B. Hezlm BY 0% v MZIW'I/V ATTORN Ys Patented Nov. 10,1942 ROLLER BEARING Lewis a. Helm, Fairfleid. Beach, Conn.

Original application July 18, 1934, Serial No.

Divided and this application November 19, 1937, Serial No. 175,389

12 Claims. (Cl. 308-212) object is to provide a device of the abovecharacter, the various parts of which can be formed from inexpensivematerials and readily assembled with a minimum expenditure of time andlabor. Another object is to provide a device of the above character inwhich machining operations are reduced to a minimum. Another object isto provide a device of the above character capable of carrying a maximumnumber of rolls or the like. Other objects will be in part obvious andin part pointed out hereinafter.

' This application is a division of my application Serial No. 735,802,filed July 18, 1934, now matured into Patent No. 2,102,460, issuedDecember 14, 1937.

The invention accordingly consists in the features of construction,combinations of elements, and arrangements of parts as will beexemplified in the structure to be hereinafter described and the scopeof the application of which will be indicated in the following claims.

In the accompanying drawing, in which is shown one or more of thevarious possible'embodiments of the mechanical features of my invention,

Figure 1 is a sectional elevation of a bearing;

Figure 2 is an end elevation of the bearing shown in Figure I, mountedon a shaft;

Figure 3 is a perspective view of the bearing shown in Figure 1 mountedon a shaft;

Figure 4 is a sectional elevation of a modified form of my bearing;

Figure 5 is a sectional elevation of another embodiment of certainfeatures of my bearing; and,

Figure 6 is an end view of the bearing shown in Figure 5. I

Similar reference characters refer to similar parts throughout theseveral views of the drawing.

As conducive to a clearer understanding of certain features of thisinvention, it might here be pointed out that the manufacture ofanti-friction devices of the above nature are characterized by variousconditions not amenable to a high production of bearings of uniformsize. Such bearings depend' for their uniformity upon various machiningoperations whereby the various diameters of the different parts of thebearing must be obtained by machining or grinding operations, for

- cordingly their ability to withstand heavy loads example, to achievethe desired size. These methods are not only slow and expensive but areproductive of errors with the result that the bearings do not have thenecessary uniformity important in devices of this nature. In addition,it is necessary to employ skilled labor to practice this manufacture andaccordingly another large item of expense is added. Furtherdifll-culties are encountered due to the fact that the rolls or balls,as the case may be, readily fall out of operative position while beinginstalled or shipped, for example, thus causing considerableinconvenience and time-consuming labor in reassembl ng the bearing.These bearings further have a small roll capacity in relation to theroll race and acin proportion to their size is considerably limited. Oneof the objects of this invention is to provide a device in which theabove difficulties, in addition to many others, are rectified.

Referring now to Figure 1, in which one embodiment of my bearingconstruction is generally indicated at 20, a race generally indicated at2| has disposed therein a plurality of rolls 22 or the like. Rolls 22are disposed about the inner periphery of a cylindrical shell 23, thisshell being preferably stamped or formed from sheet metal or the likeand. under certain conditiors. hardened by suitable heat treatment, allas will be more clearly described hereinafter. Shell 23 preferablyslightly exceeds rolls 22 in length.

Preferably I provide a sleeve-like member 24 related to shell 23preferably by a force or driven lit, thus obviating the necessity of aseparate part to retain shell 23 and sleeve 24 in related assembly and,by the same token, expediting the production and assembly of thebearing. Edges 26a and 24b of shells 26 and 24 are preferably slightlyrounded or beveled to facilitate the insertion of bearing 20 into a boreprovided for its reception. A flange-like projection 25 is preferablyintegral with sleeve 24 and extends therefrom radially toward the axisof bearing 20 a suitable distance to substantially cover the adjacentends 22a of rolls 22 as more clearly shown in Figure 2. A second sleevemember 26 substantially similar to sleeve 24 and having a flange 21 isrelated to shell 23 preferably by a force or driven fit. Thus flange 21substantially covers the adjacent ends 222) of rolls 22. Preferably theinner diameter of shell 23 and the diameters of rolls 22 are soproportioned that rolls 22 mutually sustain one an- In other,

other against radial displacement. words. each of rolls 22 acts as akeystone, and this feature, together with limitation a ainst axialdisplacement provided by flanges 25 and 21, renders the rolls immunefrom any sort of displacement, thus greatly expediting shipping andinstallation and saving the inconvenience, time I and labor ofreassembling the bearing as would be the case otherwise. Thisconstruction further obviates the necessity of providing a cage orsimilar retaining device. Furthermore, th peculiar keystone oroverlapping relation of the rolls 22 results in efficient and highlybeneficial selfalignment, as the rolls are in such close proximity thatvariation from their proper axes of rotation is precluded andaccordingly the risk of jamming is reduced to a minimum. I

As more clearly shown in Figures 2 and 3, the inner periphery of flange21 is but slightly spaced from a shaft 28 borne by bearing 20. Thus theaperture between flange 21 and shaft 28 is large enough to permit theentrance of a suitable lubricant, but is so small as to prevent theadmission of foreign particles that would be injurious to the smoothbearing surfaces of rolls 22 and shell 23.

As pointed out above, shell 23 is preferably formed from suitable flatstock which may be sheet steel. Likewise sleeves 24 and 26 arepreferably produced from the same type or kind of sheet steel. Asinexpensive manufat bure and high production are among the severalobjects of the invention, I have found it preferable to form shell 23and sleeves 24 and 26 in suitable automatics by suitably related dies.

Under certain circumstances I have found it preferable to provideabearing having a race comprised of two telescopically fitting shells.Ac-

cordingly I have provided a bearing generally in-' dicated at 42 (Figure4), having a race generally indicated at 43 comprised of a pair oftelescopically fitting shells 44 and 45 within which a number of rolls46 are disposed. Edges 44a and 44b of shell 40 are preferably slightlyrounded to facilitate the disposition of bearing 42 into a bore providedfor its reception. Extending radially toward the axis of bearing 42, Ipreferably provide a flange 41 preferably integral with shell 45 and aflange 48 preferably integral with shell 44.

necessity of providing securing means to retain.

the shells in related assembly.

The diameters of, shells 44 and 45 and those of flange construction thanthat pointed out above. Referring to Figures and 6, there is generallyindicated at 49 a bearing having a race generally indicated at 56 withinwhich are rotatably disposed a number of rolls 5| having reduced ends5|a. Race 56 is preferably comprised of a shell I 52 having rounded orbeveled edges 52a and 52b rolls 46 are preferably so proportioned thatrolls 46 may be disposed in race 43 in overlapping relationship, thatis, each roll acts as a keystone to prevent radial displacement of therolls. As flanges 41 and 48 effectively prevent axial displacement ofroll 46, the bearing, once assembled, is immune from involuntarydisassembly, I

in other words, th axes of rotation of bearing 42 and rolls 46 areconstantly parallel.

Shells 44 and 45 of race 43 may be formed in any suitable manner fromany suitable material. However, I have found it preferable to stampshells 44 and 45 from suitable sheet metal.

. Under certain conditions, I have found it preferabl to employ abearing having a different and a radial flange 53 extending inwardlytoward the axis of bearing 46. Telescopically disposed within shell 52,and preferably related thereto by a force fit, is a shell "54 having aradial flange 55 extending inwardly toward the axis of bearing 49.Flanges 53 and 55 preferably have portions 53a and 55a respectively,which extend axially toward one another preferably at a suitable angleto register with reduced ends'5la of rolls 5|. Thus where it isinconvenient to include the abovedescribed keystone relation between therolls, the provision of flanges 53 and 55 with their respectiv portions53a and 55a serve in the double capacity of maintaining the rolls inrelated assembly against radial or axial displacement. It will also beseen that flanges 53 and 55 serve as a lubricant retainer and a guardagainst the admission of injurious foreign particles as pointed outabove with respect to flanges 25 and 21 of bearing 20 in Figure 1.

While the several bearings described hereinabove may be assembled in anysuitable manner, I have found it preferable and convenient in the caseof bearing 20 (Figure 1) to force sleev 24 over shell 23 by anarborpress, for example, and thereafter insert into shell 23 a fullquota of rolls 22. As rolls 22 lie in' overlapping relation, theirdisplacement could only occur in any axial direction away from flange25. As the parts so far assembled arenow seated in the press with flange25 on the bottom, such displacement will not occur, and sleeve 26 may bereadily forced into place over shell 23, thus completing th assembly ofthe bearing.

As the assembly of bearing 42 is substantially similar to that ofbearing 49, only the assembly of bearing 42 will be described.Preferably shell 45 is placed on the table of a suitable arbor press orthe like with flange 41 downward. A full 'quota of rolls 46 is theninstalled in shell 45 wherein they will sustain one another againstradial displacement due to the above-mentioned keystone relation.Thereupon shell 44 is forceddown about shell 45 until it is incompletely assembled relation therewith.

Under certain conditions, as, for example, where the bearing will besubjected to very heavy loads and extensive use, I have found itpreferable to heat treat the sheet metal parts by a suit- .abletempering or case hardening process as desired. Upon being subjected tothe high tern-'- perature inherent in such processes, I have found thatoccasionally the sheet metal parts will warp slightly. This condition,however, is rectified in the assembly of the parts as any warping willbe ironed out when one such part is pressed over another, andaccordingly a very round and rigid bearing results.

Thus it will be seen that I have provided a bearing having a maximumroll capacity and accordingly an extremely high load capacity and longlife in proportion to its size. Furthermore the manufacture of mybearing may be carried out on a high production basis characterized byminimum expense per unit due to absence of machining operations such asgrinding or burning.

Accordingly I have provided a. construction of an essentially practicalnature in which the several objects of this invention are attained.

As many possible embodiments may be made of the above invention and asmany changes might be made in the embodiment above set forth, it is tobe understood that all matter hereinbefore set forth, or shown in theaccompanying drawing is to be interpreted as illustrative and not in alimiting sense.

I claim:

1. In roller bearing construction, in combination, a race, a pluralityof rolls in said race, the length of said rolls being no greater thanthe length of said race, said rolls being so related to said race thateach acts asa keystone for the others to prevent radial displacement, apair of sleeve members mounted about said race, and flange meansassociated with said sleeve members and adapted to register with theondsof said rolls to maintain said rolls against axial displacement.

2. In rollerbearing construction, in combination, a race, roller meansin said race, and means including flanged members force-fitted on saidrace, the flanges on said members registering with said roller means tosustain said roller means against axial displacement.

3. In roller bearing construction, in combination, a cylindrical rollrace, a plurality of rolls distributed about said race whereby each rollfunctions as a keystone for the other rolls to maintain said rollsagainst radial displacement,

said rolls being of no greater length than said race, a pair of sleevemembers forcej-fltted over sure exerted on said sleeve members by theforcefitting thereof corrects any out-oi-roundness therein, and flange'means associated with said sleeve members an'fextending radiallytherefrom toward the axis of said members, said means'being adapted toregister with the ends of said rolls to retain said rolls against axialdisplacement.

4. In roller bearing construction, in combination, a metalliccylindrical race member adapted to receive a plurality of anti-frictiondevices, a plurality of anti-friction members distributed about theinner periphery of said race member, the axis of any one oi saidanti-friction members being no greater than the axis of said race.member, metallic sleeve means iorce-fltted;over said race member,whereby the pressure resulting tromthe force-fitting of said race memberand said sleeve means corrects any out-ot-roundness therein, the axisoi. said sleeve means being no member force fitted over saidfirst-mentioned member to form a race, the force fitting of said sleevemembers being adapted to correct any outof-roundness therein, and aplurality of rolls disposed within said race between the flanges of saidmembers whereby said rolls are retained against axial displacement.

7. In roller bearing construction, in combination, a race including atleast two thicknesses of metal in the form of telescopicallyforce-fitted shells, whereby the pressure resulting from theforce-fitting of said shells corrects any out-ofroundness therein, meansforming a flange on each end of said race, and a plurality of rollsdistributed about the inner periphery of said race, said rolls beingdimensioned with respectto said inner periphery so that each roll actsas a keystone for the others to maintain the rolls in operative positionand sustain them against radial displacement.

8. In a roller bearing construction, in combination, a race,anti-friction means in said race, sleeve means fitted about said race,the outer diameterof said race being slightly larger than the innerdiameter of said sleeve means, wherebylwhen said sleeve means and saidrace are assembled, the difference in the said diameters preventsseparation thereof, and flange means on said sleeve means formaintaining said antiiriction means against axial displacement in atleast one'direction.

9. A roller bearing adapted to be inserted into a. bore or the like,said bearing comprising, in

combination, a sheet metal roll race of uniform thickness having acontinuous unbroken tracking surface, an inwardly bent in flangeintegral with said race at each end thereof, the thickness of each ofsaid flanges being less than that of said race, and a plurality of rollsdisposed about said race in tracking engagement therewith, said rollsbeing shorter than said race and so proportioned with respect to saidrace that each. roll acts as a operative tracking position in the race.

11. In roller bearing construction in accordance with claim 8, whereinthe race and the less than the axis oi said race member, and flangemeans' associated with, said sleeve means, said flange means beingadapted to register with portions oi said anti-friction members toretain said anti-iriction members against displacement irom theiroperative position in said race member.

5. In roller bearing construction, in combination, a race, flange meansassociated with said race and extending radially thereof, and aplurality 01 rolls distributed about the inner periphery or said racewhereby each roll acts as a keystone for the others to maintain saidrolls in opcrate position and sustain said rolls against radialdisplacement, said flange means being adapted to retain said rollsagainst axial displacement.

6. In roller bearing construction, in combination, a flanged sleevemember, a flanged sleeve sleeve means are of substantially equal length,flange meanson said race for cooperating with the flange means on thesleeve means to maintain said anti-friction means against axialdisplacement in either direction, said anti-friction means comprising aquota of rollers having reduced ends, both 01' said flange means beingbent toward one another axially of the bearing to engage under thereduced ends of the rollers to maintain them against radial collapse.

12. A roller bearing construction in accordance with claim 6, whereinthe rolls have reduced ends and the'flanges on the sleeve members arebent toward one another to engage under the reduced radial collapse.

, inwrsannns.

